JP6748318B1 - Escapement governor, watch movement and watch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an escapement governor, a timepiece movement, and a timepiece having excellent duration. SOLUTION: The escapement governor 13 reciprocates in a hairspring and a first rotation direction M1 and a second rotation direction M2 which are opposite to each other about a first axis O1 as the hairspring expands and contracts. 40, an escapement 14 that has an pallet fork 70 that rotates about the second axis O2, and an escape wheel 60 that can be engaged and disengaged with the pallet fork 70, and a swing seat that transmits torque from the escapement 14 to the balance with hairspring 40. 45, and. The escapement 14 applies torque to the balance with hairspring 40 by two impacts in one cycle of the balance with hairspring 40. When the difference between the torque applied from the escapement 14 to the balance with hairspring 40 minus the torque of the hairspring is defined as the balance with hairspring balance, the swing seat 45 defines the balance with the balance with balancespring torque at the end of each impact of the escapement 14. Are formed to be even. [Selection diagram] Figure 8

Description

The present invention relates to an escapement speed governor, a timepiece movement, and a timepiece.

In general, a mechanical timepiece uses a regular reciprocating rotation of a balance with hairspring to control a train wheel with a constant vibration, and is equipped with an escapement that transmits power for reciprocating rotation to a balance with hairspring. This type of escapement has evolved with repeated improvements, and various types of escapements have been proposed at present.

The club tooth lever escapement (Swiss lever escapement) is widely known as an escapement that occupies the mainstream of mechanical watches.
This escapement can be rotated mainly based on the escape wheel, the swing seat provided on the balance with hairspring, and the reciprocating rotation of the balance with hairspring, and can be disengaged from the teeth of the escape wheel. And an pallet fork having an entry nail and an exit nail. The entry claw stone and the exit claw stone can be alternately engaged and disengaged with the tooth portion of the escape wheel as the pallet fork rotates.

According to the club tooth lever escapement, as the pallet fork and the pallet fork are alternately engaged and disengaged with the teeth of the escape wheel as the pallet fork rotates, rotation of the escape wheel is prevented. It is possible to control the torque transmitted to the escape wheel and the impact at the time of contact between the teeth section of the escape wheel and the entry nail, and the teeth section of the escape wheel and the exit stone. It is possible to indirectly transmit the balance with the balance with the impact by the impact at the time of contact with the balance with the balance and replenish the balance with power.
However, it is generally known that the club tooth lever escapement has low torque transmission efficiency (escapement efficiency) from the escape wheel side to the balance with hairspring, and there is room for improvement. is there.

Therefore, in order to improve the torque transmission efficiency, for example, the rotation operating angle of the escape wheel and the teeth portion of the escape wheel and the exit nail stone at the time of contact between the teeth portion of the escape wheel and the entry nail stone There is known a club tooth lever escapement in which a rotation operating angle of an escape wheel at the time of contact is made non-uniform (for example, refer to Patent Document 1 below).
In this case, the supply balance between the amount of torque transmitted from the input nail stone to the balance with hairspring via the pallet fork and the amount of torque transmitted from the output nail stone to the balance with hairspring via the pallet fork to be optimally balanced. It can be changed, and it is possible to improve the torque transmission efficiency.

Further, as another example, for example, a two-layer structure escape wheel and a first escape wheel and a second escape wheel are coaxially overlapped, A club tooth lever escapement is known in which the tooth claws are brought into contact with each other and the tooth claws of the second escape wheel gear are brought into contact with each other (see, for example, Patent Documents 2 and 3 below).
In this case, the combination of the entry claw stone and the first escape wheel and the exit claw stone and the second escape wheel can be designed separately, and therefore, as in the case described above, Rotational operating angle of escape wheel at the time of contact between tooth part of gear wheel and entry claw stone, and rotation operating angle of escape wheel at contact of tooth part of second escape wheel and extension claw stone And can be made non-uniform, and the torque transmission efficiency can be improved.

As still another example, for example, an escape wheel having a first escape tooth and a second escape tooth formed to be displaced in the thickness direction is provided, and There is known a club tooth lever escapement for contacting the nail and the second escape wheel (for example, see Patent Document 4 below).
In this case, since the first escape wheel and the second escape wheel can be designed separately, the cancer at the time of contact between the first escape wheel and the stabbing nail is similar to the case described above. It is possible to make the rotational operating angle of the escape wheel and the rotational operating angle of the escape wheel at the time of contact between the second escape tooth and the outlaw stone uneven, thereby improving the torque transmission efficiency. It is possible.

However, each of the various club tooth lever escapements described above is a so-called indirect impact escapement that transmits torque from the escape wheel to the balance with the pallet fork, so torque transmission efficiency is not sufficient. No, there is still room for improvement.

Therefore, as an escapement having a higher torque transmission efficiency than the club tooth lever escapement, while alternately performing indirect torque transmission via the pallet fork and direct torque transmission without the pallet fork, There is known a so-called semi-indirect-semi-direct impact type escapement that transmits the torque transmitted to the balance wheel to the balance with hairspring (see, for example, Patent Documents 5 and 6 below).

The semi-indirect-semi-direct impact type escapement includes an ankle provided with a first impact pawl stone and a second impact pawl stone fixed to a balance with hairspring. The first impact pawl stone and the second impact pawl stone can be alternately contacted with the escape wheel gear as the pallet fork rotates. According to the escapement configured in this manner, the first impact pawl stone contacts the escape wheel with the rotation of the pallet fork, so that the torque transmitted to the escape wheel and the escape wheel are transferred to the escape wheel. 1 Impact It is possible to indirectly transmit to the balance with hairspring via the pallet fork by the impact at the time of contact with the nail stone, and to replenish the balance with power. Further, since the second impact pawl stone comes into contact with the tooth tip of the escape wheel as the balance with hairspring rotates, the torque transmitted to the escape wheel is generated when the escape wheel comes into contact with the second impact pawl stone. The impact can be directly transmitted to the balance with hairspring, and the balance with hairspring can be supplemented with power. Therefore, the semi-indirect-semi-direct impact type escapement is considered to have better torque transmission efficiency (escapement efficiency) than the club tooth lever escapement.

Swiss Patent Invention No. 570644 Japanese Patent No. 4894051 European Patent Application Publication No. 1914605 JP, 2018-48958, A European Patent Application Publication No. 0018796 Japanese Patent No. 6558761

By the way, in the conventional escapement, the torque transmitted from the escapement to the balance with hairspring is uneven due to the difference in impact. For this reason, when the mainspring of the power source becomes loose and the torque transmitted to the escape wheel decreases, the balance is applied from the escapement to the balance with hair at the end of the impact of one of the impacts earlier than the end of the impact of the other impact. The torque is less than the torque of the balance spring that acts on the balance with hairspring. If the torque applied from the escapement to the balance with hairspring at the end of the shock falls below the torque of the hairspring that acts on the balance with hairspring, the operation of the escapement stops without reaching the end of the shock. For this reason, in the conventional escapement, there is room for improvement in terms of suppressing the early stoppage of the operation of the escapement due to the reduction in the power of the power source and extending the duration of the operation of the escapement.

Therefore, the present invention provides an escapement governor, a timepiece movement, and a timepiece having excellent duration.

The escapement governor of the present invention includes a hairspring, a balance with the expansion and contraction of the hairspring, and a balance with a second rotating shaft which reciprocates in a first rotation direction and a second rotation direction opposite to each other about the first axis. The escapement including an escapement that rotates around an axis and an escape wheel that is engageable with and disengageable from the escapement; and a torque transmission member that transmits torque from the escapement to the balance with hair. The machine imparts a torque to the balance with at least two impacts in one cycle of the balance with hairspring, and a difference obtained by subtracting the torque of the hairspring from the torque applied to the balance with hair from the escapement is defined as a balance with balance for balance with balance with a balance. If defined, the torque transmission member has a balance with balance of balance torque at the end of impact of each impact of the escapement at any point until the mainspring is unwound and the escapement is stopped. Is formed.

According to the present invention, even if the torque applied to the balance with hairspring from the escapement decreases as the torque transmitted from the power source to the escape wheel decreases, any impact of the escapement will cause a greater impact than other impacts. It is possible to suppress the torque shortage at the end of the shock as soon as possible. Therefore, it is possible to suppress a state in which the impact cannot be ended earlier than any other impact of the escapement. Therefore, the duration of the escapement governor can be improved.

In the escapement governor, the torque transmission member may rotate integrally with the balance with hairspring.

According to the present invention, it is possible to efficiently transmit the torque from the escapement to the balance with hairspring, as compared with a configuration in which gears are meshed with each other on the torque transmission path from the torque transmitting member to the balance with hairspring.

In the escapement governor, the escape wheel & pintle contacts the torque transmission member to apply torque to the balance with hairspring when the balance with hairspring rotates in the first rotation direction, and the balance with hairspring is When rotating in the second rotation direction, it may come into contact with the pallet fork to apply torque to the balance with hairspring.

According to the present invention, since the escapement can be configured as a so-called semi-indirect-semi-direct impact type, the escapement having excellent torque transmission efficiency as compared with the case where the escapement is configured as a so-called indirect impact type. It can be a governor.

In the escapement governor, the escape wheel comes into contact with the pallet fork when the balance with hairspring rotates in the first rotation direction and when the balance with hairspring rotates in the second rotation direction. May be given.

According to the present invention, the escapement governor equipped with a so-called indirect impact type escapement such as a club tooth lever escapement that transmits torque only from the escape wheel to the balance with the balance through the pallet fork. Can be improved.

In the escapement speed governor, the torque transmission member includes a swinging rock that can be engaged with and disengaged from the pallet fork, and the center of the swinging rock is located on the balance with hairspring when viewed from the axial direction of the first axis. It may be arranged at a position deviated around the first axis with respect to an imaginary straight line passing through the first axis and the second axis in a stationary state in which the torque of the balance spring is not applied.

When viewed from the axial direction of the first axis, in the configuration in which the center of the swaying stone is arranged on a virtual straight line passing through the first axis and the second axis in a stationary state, the difference in the rotating direction of the balance with hairspring (difference in impact) This causes a difference in balance of balance with hairspring torque at the end of impact. According to the present invention, it is possible to arrange the torque transmission member so that the balance with hairspring torque at the end of each impact of the escapement is even. Therefore, the above-described effects can be obtained.

In the above escapement speed governor, when viewed from the axial direction, the center of the swing rock is displaced from the virtual straight line in the stationary state by more than 0° and not more than 15° around the first axis. It may be arranged at a different position.

Here, the position of the torque transmission member when the balance with hairspring is in a stationary state is defined as a stationary position. According to the present invention, after the stop of the escape wheel & pinion, the escapement governor can be formed such that the torque transmission member passes through the stationary position during impact. As a result, when the torque transmitted from the power source to the escape wheel decreases, the escape wheel stops at the position during impact, ensuring restartability when increasing the torque transmitted to the escape wheel. can do.

The escapement governor may include an adjusting unit that adjusts the position of the torque transmission member around the first axis.

According to the present invention, since the torque transmission member can be arranged so that the balance with hairspring torque at the end of each impact of the escapement can be equalized, the above-described effects can be obtained.

In the escapement governor, the torque transmission member is fixedly arranged with respect to the balance with hairspring, and the adjusting means is a support member that rotatably supports the balance with hairspring and an outer peripheral portion of the balance spring. It may have a fixed whisker and a whisker receiver mounted on a peripheral surface of the support member extending around the first axis to support the whistle.

According to the present invention, the position of the balance with hairspring and the torque transmitting member with respect to the support member can be adjusted with respect to the support member by adjusting the position of the balance with respect to the support member when the whisker holder is assembled to the support member.

In the above escapement speed governor, the torque transmission member is fixedly arranged with respect to the balance with hairspring, and the adjusting means is attached to the shaft portion of the balance with hairspring and the shaft portion, and is provided in the balance spring. And a beard ball fixed to the end portion.

According to the present invention, when the whisker ball is assembled to the shaft portion of the balance with hairspring, the positions of the balance with hairspring and the torque transmission member with respect to the support member can be adjusted by adjusting the positions around the first axis line with respect to the shaft portion. ..

In the escapement governor, the balance with hairspring has a shaft portion, the torque transmission member has a mounting portion mounted on the shaft portion of the balance with hairspring, the adjusting means, the shaft portion of the balance with hairspring. And the mounting portion.

According to the present invention, when the mounting portion of the torque transmission member is assembled to the shaft portion of the balance with hairspring, the position of the torque transmission member with respect to the balance with the first axis line is adjusted by adjusting the position around the first axis line with respect to the shaft portion. The position around the first axis of the torque transmission member with respect to the support member can be adjusted.

A timepiece movement of the invention includes the escapement governor described above.
A timepiece of the invention includes the above-described timepiece movement.

According to the present invention, since the escapement governor having an excellent duration is provided, it is possible to provide a timepiece movement and a timepiece having a long duration.

According to the present invention, it is possible to provide an escapement governor, a timepiece movement, and a timepiece having excellent duration.

It is a top view which shows the timepiece which concerns on embodiment. It is the top view which looked at the movement which concerns on embodiment from the front side. It is the perspective view which looked at the escapement governor concerning an embodiment from the front side. It is the top view which looked at the governor concerning an embodiment from the front side. It is sectional drawing in the VV line of FIG. It is the perspective view which looked at the balance with hairspring and the swing seat which concern on embodiment from the front side. It is the perspective view which looked at the escapement governor concerning an embodiment from the back side. It is the top view which looked at the escapement and swing seat which concern on embodiment from the front side. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a top view explaining operation of the escapement governor concerning an embodiment. It is a graph which shows the balance torque balance at the end of each impact of the escapement. In the escapement governor concerning an embodiment, it is a graph which shows the torque which acts on a balance with hairspring at the time of direct impact. In the escapement governor concerning an embodiment, it is a graph which shows the torque which acts on a balance with hairspring at the time of an indirect impact. It is a graph which shows the torque which acts on a balance with hairspring at the time of direct impact in the escapement governor concerning a comparative form. It is a graph which shows the torque which acts on the balance with hairspring at the time of indirect impact in the escapement governor concerning a comparative form. In the escapement governor concerning the modification of an embodiment, it is a graph which shows the torque which acts on balance with hairspring at the time of direct impact. In the escapement governor concerning the modification of an embodiment, it is a graph which shows the torque which acts on the balance with hairspring at the time of an indirect impact.

Embodiments according to the present invention will be described below with reference to the drawings. In the present embodiment, a mechanical timepiece will be described as an example of the timepiece.

Generally, a mechanical body including a driving part of a timepiece is called a "movement". A state in which a dial and hands are attached to this movement and put in a watch case to make a finished product is called a "complete" of the watch. Of both sides of the main plate that constitutes the watch substrate, the side of the watch case on which the glass is present (that is, the side on which the dial is present) is called the "back side" of the movement. Further, of both sides of the main plate, the side of the watch case where the case back is provided (that is, the side opposite to the dial) is referred to as the “front side” of the movement. In the present embodiment, the direction from the dial to the case back is defined as upward and the opposite side is defined as downward.

FIG. 1 is a plan view showing a timepiece according to an embodiment.
As shown in FIG. 1, the complete watch 1 of the present embodiment has a movement (timepiece movement) 10 and a scale indicating at least time information in a timepiece case composed of a case back and glass 2 not shown. The dial 3 and the hands including the hour hand 5, the minute hand 6 and the second hand 7 are provided.

FIG. 2 is a plan view of the movement according to the embodiment seen from the front side. It should be noted that in FIG. 2, some of the components constituting the movement 10 are omitted for clarity.
As shown in FIG. 2, the movement 10 has a base plate 11 that constitutes a substrate. The movement 10 includes a front train wheel 12 and an escapement speed governor 13 on the front side of the main plate 11.

The front train wheel 12 mainly includes a barrel wheel 20, an idle gear 21, a second wheel 22, a third wheel 23, a fourth wheel 24, and an escape wheel intermediate wheel 25. The barrel wheel 20 is pivotally supported between the main plate 11 and a barrel holder (not shown), and a mainspring (power source) (not shown) is housed therein. The mainspring is wound up by the rotation of the winding stem 27 connected to the crown 26 shown in FIG.

The idle gear 21, the second wheel 22, the third wheel 23, the fourth wheel 24, and the escape wheel intermediate wheel 25 are pivotally supported between the main plate 11 and a train wheel bridge (not shown). The idle gear 21, the second wheel 22, the third wheel 23, the fourth wheel 24, and the escape wheel intermediate wheel 25 rotate based on this rotation when the barrel wheel 20 rotates due to the elastic restoring force of the wound mainspring. To do.

That is, the idle gear 21 meshes with the barrel wheel 20, and rotates based on the rotation of the barrel wheel 20. The center wheel & pinion 22 meshes with the idle gear 21, and rotates based on the rotation of the idle gear 21. The third wheel & pinion 23 meshes with the second wheel & pinion 22, and rotates based on the rotation of the second wheel & pinion 22. The fourth wheel & pinion 24 meshes with the third wheel & pinion 23 and rotates based on the rotation of the third wheel & pinion 23. The second hand 7 shown in FIG. 1 is attached to the fourth wheel & pinion 24, and the second hand 7 displays "second" based on the rotation of the fourth wheel & pinion 24. The second hand 7 rotates once per minute at the rotational speed controlled by the escapement governor 13.

When the fourth wheel & pinion 24 rotates, a minute indicator (not shown) rotates based on this rotation. The minute hand 6 shown in FIG. 1 is attached to the minute wheel, and the minute hand 6 displays "minute" by the rotation of the minute wheel. The minute hand 6 rotates once per hour at the rotation speed regulated by the escapement governor 13.

When the minute driving wheel rotates, the day driving wheel (not shown) rotates based on this rotation, and further the hour wheel (not shown) rotates based on the rotation of the day driving wheel. The hour wheel 5 shown in FIG. 1 is attached to the hour wheel, and the hour hand 5 displays "hour" as the hour wheel rotates. The hour hand 5 rotates once every 12 hours at the rotational speed controlled by the escapement governor 13.

The escape wheel intermediate wheel 25 meshes with the fourth wheel & pinion 24 and rotates based on the rotation of the fourth wheel & pinion 24. The escape wheel intermediate wheel 25 meshes with an escape wheel kana 61 (see FIG. 3) of an escape wheel 60 described later.

FIG. 3 is a perspective view of the escapement governor according to the embodiment as viewed from the front side. In FIG. 3, the balance wheel 42, which will be described later, is shown by an imaginary line in order to make the drawing easy to see, and a part of the balance wheel 42 is omitted.
As shown in FIGS. 2 and 3, the escapement governor 13 includes an escapement 14 that controls the rotation of the front train wheel 12, a governor 15 that controls the escapement 14, and an escapement. The swing seat 45 (torque transmission member) that transmits torque from the balance gear 14 to the balance with hairspring 40 of the speed governor 15.

FIG. 4 is a plan view of the governor according to the embodiment as viewed from the front side. FIG. 5 is a sectional view taken along line VV of FIG.
As shown in FIG. 4 and FIG. 5, the speed governor 15 includes a balance spring 30, a balance holding unit 33 that holds an outer end portion of the balance spring 30, and a first axis O1 according to expansion and contraction of the balance spring 30. A balance with hairspring 40 that reciprocally rotates around a center and a balance with hairspring 16 (support member) that is fixed to the main plate 11 (see FIG. 2) and rotatably supports the balance with hairspring 40. The balance spring 30 is spirally wound, and a bead 31 is fixed to the inner end thereof, and a beard 34 is fixed to the outer end 30a. The beard holder 34 may be fixed to the outer peripheral portion of the hairspring 30.

The beard support unit 33 includes a beard support 34 and a beard support 35 that supports the beard support 34. The beard holder 35 is fixedly arranged with respect to the main plate 11. Specifically, the beard holder 35 is supported by the balance with hair bridge 16. The beard-bearing receiver 35 is attached to the outer peripheral surface 16a of the shaft portion of the balance with hair bridge 16 that extends around the first axis O1 via an annular beard-bearing seat 36. Note that the beard-bearing receiver 35 may be attached to the outer peripheral surface or the inner peripheral surface of the balance with hair bridge 16 which extends around the first axis O1 without using the beard-bearing seat 36. The beard holder 35 has a beard arm 37 that holds the beard 34. The beard holding arm 37 is formed with a slit 37 a that penetrates vertically. A cylindrical beard holding member 38 is fitted in the slit 37a.

The beard holder 34 is inserted inside the beard holder 38, and is stably held by the beard holder 38 in a state where it is prevented from coming off by a beard screw 39. The beard holder 34 holds the outer end portion of the hairspring 30 by, for example, bonding or caulking. Accordingly, the outer end portion of the balance spring 30 is fixedly arranged with respect to the balance with hair bridge 16 and the main plate 11.

The balance with hairspring 40 includes a balance stem 41 (shaft portion) and a balance wheel 42. The balance with hairspring 40 is pivotally supported between the main plate 11 and the balance with hairspring bridge 16. The balance with the hairspring 30 as a power source is reciprocally rotated (forward/reverse rotation) around the first axis O1 with a steady amplitude (swing angle) according to the output torque of the barrel wheel 20.

Specifically, as shown in FIG. 4, the balance 40 reciprocates in a first rotation direction M1 and a second rotation direction M2 that are opposite to each other about the first axis O1. In the present embodiment, in a plan view seen from the front side of the movement 10, the direction in which the balance with hairspring 40 rotates clockwise about the first axis O1 is referred to as a first rotation direction M1, and the direction in which it rotates counterclockwise is referred to as a first rotation direction M1. Two rotation directions M2.

As shown in FIG. 5, the balance stem 41 is axially supported by the main plate 11 and the balance bridge 16 at both ends in the axial direction. A balance ball 31 is attached to the balance 41. As a result, the inner end portion of the balance spring 30 is fixedly arranged with respect to the balance with hairspring 40. The beard ball 31 is attached to the outer peripheral surface 41a of the balance 41 that extends around the first axis O1. A balance wheel 42 is fixed to the balance 41. The balance wheel 42 is externally fitted to the balance 41 below the bead 31. The shape of the balance wheel 42 is not limited to the illustrated example, and may be freely changed.

As shown in FIG. 3, a small collar 43 is formed below the outer fitting portion of the balance wheel 42 of the balance 41. The small collar 43 is formed in a cylindrical shape so that the rotation locus has a smaller diameter than the swing seat 45. In the portion of the small collar 43 that corresponds to the swaying stone 50 described later in the radial direction, a curved rattling 43a that is recessed in a curved shape is formed on the inner side in the radial direction (see also FIG. 6). The rattle 43a functions as an escape portion that prevents a sword tip 82, which will be described later, from coming into contact with the small brim 43 when an uncle box 81 (see FIG. 8), which will be described later, is engaged with the swing stone 50. Further, the sword tip 82 can be slidably contacted with a portion of the outer peripheral surface of the small brim 43 excluding the rattle 43a.

FIG. 6 is a perspective view of the balance with hairspring and the swing seat according to the embodiment as seen from the front side. Note that, in FIG. 6, the flywheel 42 is shown by an imaginary line in order to make the drawing easy to see.
As shown in FIG. 6, the swing seat 45 is provided coaxially with the balance with hairspring 40 so as to be integrally rotatable. The swing seat 45 includes a swing seat body 46 (mounting portion) fixed to the balance 41, and a swing stone 50 and a contact pawl stone 55 fixed to the swing seat body 46.

The swing body 46 is attached to the balance 41. The swing seat body 46 is adjacent to the lower side of the small collar 43 of the balance 41. The swing body 46 is arranged at a height corresponding to the escape wheel 60. The swing body 46 is made of, for example, a metal material or a material having a crystal orientation such as single crystal silicon. Examples of the manufacturing method of the swing body 46 include electroforming, LIGA process incorporating an optical method such as photolithography, DRIE, metal powder injection molding (MIM), and the like. However, the present invention is not limited to this case, and the swing seat body 46 may be formed by another method.

The swing seat body 46 is formed with a through hole 47 penetrating vertically and a slit 48 extending in the radial direction and having a U-shape so as to open to the outside in the radial direction. The through hole 47 has a flat surface on the outer side in the radial direction and a semicircular shape that bulges in an arc on the inner side in the radial direction when viewed in the axial direction of the first axis O1.

The swing stone 50 is press-fitted into the through hole 47. The swing stone 50 is formed in a semicircular shape in plan view having a flat surface 51 on the outer side in the radial direction and an arcuate surface 52 on the inner side in the radial direction, corresponding to the shape of the through hole 47. The swing stone 50 is formed of an artificial jewel such as ruby. The swing stone 50 is formed so as to extend upward from the swing seat body 46. As a result, the swing rock 50 can be brought into contact with the pallet fork 70, which will be described later, arranged above the escape wheel 60 (see FIG. 3 ). The swing rock 50 reciprocally rotates about the first axis O1 in synchronization with the balance with hairspring 40, and releasably engages with an uncle box 81 (see FIG. 8) described later in the middle thereof.

The contact pawl stone 55 is inserted into the slit 48 of the swing seat body 46 and is fixed by, for example, an adhesive or the like. The contact pawl stone 55 is formed of an artificial jewel such as ruby as with the swing stone 50. The contact pawl stone 55 is formed in a rectangular plate shape extending in the radial direction around the first axis O1. The tip of the contact pawl stone 55 projects outward in the radial direction from the outer peripheral edge of the swing seat body 46. The contact pawl stone 55 is capable of contacting an escape wheel 63 (see FIG. 3) described later of the escape wheel 60, and is a pawl stone for transmitting the torque transmitted to the escape wheel 60 to the balance with hairspring 40. It is said that.

As shown in FIGS. 3 and 6, the side surface of the tip of the contact pawl stone 55 facing the second rotation direction M2 is formed flat along the radial direction, and the working surface 63a of the escape tooth 63 is formed. Are contact surfaces 56 capable of contacting (colliding) with each other. Further, an inclined surface 57 facing the first rotation direction M1 side is formed at the tip of the contact pawl stone 55. The contact pawl stone 55 is fixed in the slit 48 so as not to project above the swing seat body 46. This prevents the contact pawl stone 55 and the pallet fork 70 described below from coming into contact with each other.

The contact pawl stone 55 repeats the approach and the retreat with respect to the rotation locus R (see FIG. 8) of the escape wheel 64, which will be described later, by the rotation of the balance with hairspring 40. Thereby, the action surface 63a of the escape wheel 63 of the escape wheel 64 can be brought into contact (collision) with the contact surface 56 of the contact pawl stone 55. When the action surface 63a of the escape wheel 63 comes into contact with the contact surface 56 of the contact pawl stone 55, torque is transmitted from the escape wheel 60 to the contact pawl stone 55.

FIG. 7 is a perspective view of the escapement governor according to the embodiment as viewed from the back side.
As shown in FIGS. 3 and 7, the escapement 14 is based on the rotation of the escape wheel & pinion 60 and the balance with hairspring 40, which are rotated by the torque transmitted from the mainspring of the barrel wheel 20 via the front train wheel 12. An pallet 70 that rotates to rotate and stop the escape wheel 60. Hereinafter, the rotation axis of the pallet fork 70 will be referred to as a second axis O2, and the rotation axis of the escape wheel 60 will be referred to as a third axis O3.

The escape wheel 60 is integrally formed with an escape wheel shaft portion 62 in which an escape wheel kana 61 that meshes with the escape wheel intermediate wheel 25 (see FIG. 2) is formed, and by pressing the escape wheel shaft portion 62, for example. , And an escape wheel gear 64 having a plurality of escape wheel teeth 63. In the present embodiment, an example is described in which the escape tooth 63 has eight teeth and the escape wheel 61 has ten teeth. However, the invention is not limited to this case, and the number of teeth of the escape tooth 63 and the escape wheel 61 may be changed as appropriate.

Further, in the present embodiment, the escape wheel & pinion 60 rotates counterclockwise around the third axis O3 as viewed from the front side by the torque transmitted from the escape wheel & pinion intermediate wheel 25 side via the escape wheel and pinion 61. The case will be described as an example. The direction rotating counterclockwise about the third axis O3 is called counterclockwise M3, and the opposite direction is called clockwise M4. Furthermore, the rotation locus R drawn by the tooth tips of the escape wheel 63 as the escape wheel 60 rotates is simply referred to as the rotation trajectory R of the escape wheel 64 (see FIG. 8).

The escape wheel & pinion 60 is pivotally supported by the main plate 11 (see FIG. 2) and a train wheel bridge (not shown) at both ends of the escape wheel & pinion shaft portion 62 in the axial direction.

The escape wheel 64 is made of, for example, a metal material, a material having a crystal orientation such as single crystal silicon, or the like, like the swing seat 46. Examples of a method for manufacturing the escape wheel 64 include electroforming, a LIGA process incorporating an optical method such as a photolithography technique, DRIE, and metal powder injection molding (MIM). However, the invention is not limited to this case, and the escape wheel 64 may be formed by another manufacturing method.

The escape wheel gear 64 has an insertion hole 65a formed in the central portion thereof, and an annular hub portion 65 through which the escape wheel shaft portion 62 is assembled by press fitting or the like through the insertion hole 65a, and an outer side in the radial direction from the hub portion 65. And eight spoke portions 66 that are arranged at equal intervals in the circumferential direction and that are formed integrally with the hub portion 65 and the spoke portions 66.

The spoke portion 66 is formed so as to taper toward the outside in the radial direction, and the tip end portion thereof is formed to be slightly bent in the counterclockwise direction M3. The tip portions of the spoke portions 66 function as escape tooth 63. As a result, the escape wheel & pinion 60 of the present embodiment has escape wheel teeth 63 with eight teeth. Of the escape tooth 63, the side surface facing the counterclockwise direction M3 makes contact with the contact pawl stone 55 and an action surface 63a that engages with an input pawl stone 72 and an eject pawl stone 73 described later. Has been done.

The escape wheel & pinion 60 configured as described above directly transmits the torque transmitted from the escape wheel intermediate wheel 25 side to the balance with hairspring 40 when the balance with hairspring 40 rotates in the first rotation direction M1. At the same time, when the balance with hairspring 40 rotates in the second rotation direction M2, it plays a role of indirectly transmitting the torque transmitted from the fourth wheel & pinion 24 side to the balance with hairspring 40 via the pallet fork 70.

The pallet fork 70 controls the rotation of the escape wheel & pinion 60, that is, the start and the stop of the rotation of the escape wheel & pinion 60. The pallet fork 70 includes an entry claw stone 72 and an exit claw stone 73 that can be engaged with and disengaged from the escape tooth 63. Further, the pallet fork 70 is provided with a pallet fork 75 which is a rotating shaft, and a pallet fork 78 having two pallet fork beams 76A and 76B and a positioning arm 77.

The pallet fork 75 is arranged coaxially with the second axis O2. The pallet fork 75 is axially supported by the main plate 11 and a pallet fork (not shown) at both ends in the axial direction.

The pallet fork 78 is fixed to the pallet true 75 by, for example, press fitting. The pallet fork 78 is formed in a plate shape by, for example, electroforming or a MEMS technique, and is arranged above the escape wheel 60 and the swing seat 46. An insertion hole for fixing the pallet truer 75 is formed in a connecting portion 79 of the two pallet fork beams 76A and 76B in the pallet fork 78. The pallet fork 78 is fixed integrally with the pallet fork 75 by fitting the pallet fork 75 into the insertion hole by press fitting or the like.

FIG. 8 is a plan view of the escapement and swing seat according to the embodiment as viewed from the front side. Note that, in FIG. 8, the sword tip 82 is shown by an imaginary line in order to make the drawing easy to see.
As shown in FIG. 8, one pallet beam 76A moves from the connecting portion 79, to which the pallet true 75 is fixed, toward the clockwise M4 side opposite to the rotation direction of the escape wheel 60, that is, the swing seat 45. It is formed so as to extend toward the side. The other pallet fork beam 76B is formed to extend from the connection portion 79 to which the pallet fork 75 is fixed, toward the counterclockwise M3 side, which is the rotation direction of the escape wheel 60. The arm 77 is formed so as to extend from the connecting portion 79, to which the pallet fork 75 is fixed, in a direction away from the escape wheel & pinion 60.

A pair of stag beetles 80 arranged side by side in the circumferential direction of the second axis O2 are provided at the tip of one of the pallet fork beams 76A. An inner side of the stag beetle 80 is an ankle box 81 that opens toward the small brim 43 side of the balance 41 and houses a swinging stone 50 that moves with the reciprocating rotation of the balance with hairspring 40 in a detachable manner.

Further, a sword tip 82 is attached to the tip of one of the pallet fork beams 76A. The sword tip 82 is fixed to the pallet fork beam 76A by being fitted into the tip portion of the one pallet beam 76A from above by, for example, press fitting. However, the present invention is not limited to this case, and the sword tip 82 may be fixed to the tip portion of one of the pallet beam 76A by using an adhesive, caulking or the like.

The sword tip 82 is located between the pair of stag beetles 80 in a plan view (that is, positioned inside the pallet box 81), and extends slightly beyond the stag beet 80 toward the small collar 43 side of the balance 41. The sword tip 82 is positioned above the swing stone 50 and fixed so as to be positioned at the same height as the small brim 43 of the balance stem 41. The tip of the sword tip 82 is radially opposed to a part of the outer peripheral surface of the small brim 43 excluding the rattle 43a while the swing stone 50 is separated from the pallet fork 81. In the state where the swinging stone 50 is engaged with the pallet fork 81, the swinging stone 50 is housed in the gravel 43a.

When the swinging stone 50 is separated from the pallet fork 81, the tip of the sword tip 82 faces the outer peripheral surface of the small collar 43 in the radial direction with a slight gap, so that, for example, the balance with hairspring 40 is used. Even if disturbance is input during free vibration and the stop of the pallet fork 70 is released due to the influence of the disturbance, the tip of the sword tip 82 can be brought into direct contact with the outer peripheral surface of the small collar 43. Accordingly, the displacement of the pallet fork 70 due to the disturbance can be suppressed, and the stop of the pallet fork 70 can be prevented from being released.

Further, in one of the pallet fork beams 76A, a stone attachment hole 83 for fixing the pallet stone 72 is formed in a portion located closer to the pallet fork 75 than the sword tip 82. The stone mounting hole 83 is formed so as to vertically penetrate the pallet beam 76A. The insert nail stone 72 is detachable from the operating surface 63a of the escape wheel 63 of the escape wheel 64, and is used as a nail stone for stopping and canceling the escape wheel 60. ..

The claw stone 72 is formed of an artificial jewel such as ruby like the swing stone 50, and is fixed in the stone mounting hole 83 by, for example, press fitting, or is fixed by an adhesive or the like. The pallet stone 72 is formed in a rectangular column shape extending downward from the pallet beam 76A, and is fixed so as to reach the same height as the escape wheel 60. The side surface of the insert pawl stone 72 facing the clockwise direction M4 side opposite to the rotation direction of the escape wheel 60 is engaged with the action surface 63a of the escape wheel 63 of the escape wheel 64. The surface 72a is formed.

At the tip of the other pallet beam 76B, a slit 85 for fixing the protruding nail 73 is formed. The slit 85 is formed so as to vertically penetrate the pallet fork beam 76B and open toward the escape wheel 60 side. The talc stone 73 is a pawl stone that can be engaged with and disengaged from the action surface 63a of the escape wheel 63 in the escape wheel 64, and is for stopping and canceling the escape wheel 60, It is a nail stone for transmitting the torque transmitted to the escape wheel 60 to the balance with hairspring 40 via the pallet fork 70.

Similar to the swing stone 50, the talc stone 73 is formed of an artificial jewel such as ruby, and is fixed in the slit 85 by, for example, press fitting, or is fixed by an adhesive or the like. The protruding claw stone 73 is formed in a rectangular plate shape extending along the slit 85, and is fixed so as to project toward the escape wheel 60 side with respect to the pallet beam 76B. Further, the talc stone 73 is formed so as to extend downward from the pallet beam 76B, and is fixed so as to reach the same height as the escape wheel 60.

An engaging surface 73a and a sliding surface 73b are formed at the tip of the protruding nail 73 so as to face the clockwise direction M4 opposite to the rotation direction of the escape wheel 60. The engagement surface 73a is formed flat along the slit 85, and the action surface 63a of the escape wheel 63 of the escape wheel 64 can be engaged with the engagement surface 73a. The sliding surface 73b is located closer to the escape wheel 60 than the engagement surface 73a, and is the rotation direction of the escape wheel 60 from the slit 85 side toward the escape wheel 60 side. It is an inclined surface formed so as to extend toward the counterclockwise direction M3 side, and the escape tooth 63 is slidable.

Specifically, the escape wheel 63 of the escape wheel 60 is configured to slide on the sliding surface 73b after the engagement with the engagement surface 73a is released. The operating surface 63a of the escape wheel 63 slides on the sliding surface 73b, so that torque is transmitted from the escape wheel 60 to the side of the protruding stone 73.

The pallet fork 70 configured as described above rotates about the second axis O2 based on the rotation of the balance 40 as described above. Specifically, the pallet fork 70 rotates about the second axis O2 in the direction opposite to the rotation direction of the balance with hairspring 50, which is moved by the reciprocating rotation of the balance with hairspring 40. At this time, the entry claw stone 72 and the exit claw stone 73 alternately repeat the entry and the retraction with respect to the rotation locus R of the escape wheel 64 by the rotation of the pallet fork 70. Thereby, the action surface 63a of the escape wheel 63 of the escape wheel 64 can be engaged with the engagement surface 72a of the entry pawl stone 72 or the engagement surface 73a of the ejection pawl stone 73. Become. In particular, since the entry nail stone 72 and the exit nail stone 73 are arranged so as to sandwich the second axis O2, when the escape tooth 63 and the entry nail stone 72 are engaged, the exit nail stone 73 is arranged. When the escape tooth 63 is disengaged from the escape tooth 63 and the escape tooth 63 and the protruding nail stone 73 are engaged with each other, the entry nail stone 72 is detached from the escape tooth 63.

More specifically, when the balance with hairspring 40 rotates in the first rotation direction M1, the engagement between the escape tooth 63 and the entry pawl stone 72 is released, and the escape tooth 63 and the contact pawl stone 55 are separated from each other. After contacting with each other, the escape tooth 63 and the protruding nail stone 73 are engaged with each other. Further, when the balance with hairspring 40 rotates in the second rotation direction M2, the engagement between the escape tooth 63 and the protruding nail stone 73 is released, and the escape tooth 63 is moved by the sliding surface 73b of the protruding nail stone 73. After sliding relative to the upper part, the escape tooth 63 and the pallet stone 72 engage with each other. This point will be described in detail later.

Further, the escapement 14 includes a dope pin 90 that positions the pallet fork 70 when the entry claw stone 72 and the exit claw stone 73 engage with the escape wheel gear 64 of the escape wheel 60. The dote pin 90 is arranged on the opposite side of the escape wheel 60 with the one of the pallet fork beams 76A interposed therebetween. The dote pin 90 is arranged between the one pallet beam 76A and the arm 77 in a plan view with a space between the one pallet beam 76A and the arm 77. The dote pin 90 is fixed so as to project upward from the main plate 11, for example, and is positioned at the same height as the pallet fork 78.

Since the dote pin 90 is arranged in this way, one of the pallet beam 76A and the arm 77 can come into contact with the dope pin 90. This makes it possible to regulate the rotation of the pallet fork 70 and position it.

In the escapement speed governor 13 configured as described above, when viewed from the axial direction of the first axis O1, the center C of the swing rock 50 is in a stationary state in which the torque of the balance spring 30 does not act on the balance with hairspring 40. Then, it is arranged at a position deviated by a predetermined angle θ around the first axis O1 with respect to the virtual straight line L passing through the first axis O1 and the second axis O2. Specifically, when viewed from the axial direction of the first axis O1, the center C of the rocking stone 50 is arranged at a position deviated by a predetermined angle θ with respect to the virtual straight line L in the second rotation direction M2. The predetermined angle θ is greater than 0° and 15° or less. Accordingly, the swing seat 45 is formed so that the balance with balance with hairspring at the end of each impact of the escapement 14 becomes even. This point will be described in detail later. The center C of the swing stone 50 when viewed from the axial direction of the first axis O1 is the center between both ends of the swing stone 50 in the circumferential direction around the first axis O1.

Returning to FIG. 5, the escapement governor 13 includes a plurality of adjusting means 101, 102, 103 for adjusting the position of the swing seat 45 around the first axis O1. The first adjusting means 101 includes a balance bridge 16, a beard holder 34, and a beard holder 35. The first adjusting means 101 adjusts the position around the first axis O1 with respect to the balance bridge 16 when assembling the balance support 35 to the balance bridge 16, so that the balance spring 30, balance with hairspring 40, and swing seat for the balance bridge 16 are adjusted. The position of 45 can be adjusted. The second adjusting means 102 includes a balance 41 and a beard ball 31. The second adjusting unit 102 adjusts the positions of the balance with hairspring 40 and the swing seat 45 with respect to the balance with hairspring 16 by adjusting the positions around the first axis O1 with respect to the balance with hairspring 41 when the balance ball 31 is assembled to the balance with hairspring 41. it can. The third adjusting means 103 includes a balance 41 and a swing seat body 46. The third adjusting means can adjust the position of the swing seat 45 with respect to the balance with hairspring 40 by adjusting the position around the first axis O1 with respect to the balance stem 41 when the swing seat body 46 is assembled to the balance stem 41. The position of the center C of the swing stone 50 when viewed from the axial direction of the first axis O1 is adjusted by at least one of the plurality of adjusting means 101, 102, 103.

Next, the operation of the escapement governor 13 configured as described above will be described with reference to FIGS. 9 to 20. 9 to 20 are plan views illustrating the operation of the escapement governor according to the embodiment.
In the operation start state in the following description, as shown in FIG. 9, the action surface 63a of the escape tooth 63 is engaged with the engagement surface 72a of the pallet stone 72, and the arm 77 of the pallet fork 70 is provided. Touches the dope pin 90 to position the pallet fork 70. As a result, rotation of the escape wheel & pinion 60 is stopped. Further, the swinging stone 50 moves in the first rotation direction M1 due to the free vibration of the balance with hairspring 40 and enters the inside of the pallet fork 81. The contact pawl stone 55 is retracted from the rotation locus R of the escape wheel 64.

From such an operation start state, the operation of the escapement governor 13 associated with the reciprocating rotation of the balance with hairspring 40 will be described step by step.

When the balance with hairspring 40 is further rotated in the first rotation direction M1 by the elastic energy stored in the balance spring 30 from the state shown in FIG. While contacting and engaging with the inner surface of the stag beetle 80 side located in the traveling direction, the pallet anchor 81 is pressed in the first rotation direction M1. As a result, the torque of the balance spring 30 is transmitted to the pallet fork 70 via the swing stone 50. When the pallet fork 81 and the rocking stone 50 are engaged, the small brim 43 and the sword tip 82 do not come into contact with each other because the rattle 43a is formed. Therefore, the torque of the balance spring 30 can be efficiently transmitted to the pallet fork 70.

As a result, as shown in FIG. 10, the pallet fork 70 rotates counterclockwise around the second axis O2 as viewed from the front side, and the arm 77 of the pallet fork 70 separates from the dope pin 90. Further, as the pallet fork 70 rotates, the pawl stone 72 moves in the direction in which it separates from the escape wheel 64 (the direction in which it retracts from the rotational trajectory R of the escape wheel 64). Then, by moving the insert pawl stone 72 to a position slightly deviated from the rotation locus R of the escape wheel 64, the insert pawl stone 72 is disengaged from the escape tooth 63 and the escape tooth 63 The engagement can be released. Thereby, the stop of the escape wheel & pinion 60 can be released.

When the engagement tooth 63 is disengaged from the entry pawl stone 72, the entry pawl stone 72 has a pulling angle, so the escape wheel & pinion 60 is in the counterclockwise direction M3 which is the original rotation direction. Instead, it momentarily retracts in the opposite clockwise direction M4. The escape wheel & pinion 60 resumes rotation in the counterclockwise direction M3 by the torque transmitted via the front train wheel 12 after the momentary backward movement. Thus, by instantaneously retracting the escape wheel & pinion 60, the meshing of the front train wheel 12 can be made more reliable, and the front train wheel 12 can be operated stably and with high reliability.

Then, as shown in FIG. 11, when the escape wheel & pinion 60 restarts to rotate in the counterclockwise direction M3, the rotation locus R of the escape wheel gear 64 is accompanied by the rotation of the balance with hairspring 40 in the first rotation direction M1. The action surface 63a of the escape tooth 63 comes into contact (collision) with the contact surface 56 of the contact pawl stone 55 that has entered inside. The torque transmitted to the escape wheel 60 by the impact at the time of contact between the contact pawl stone 55 and the escape wheel 63 can be directly transmitted to the balance with hairspring 40 via the swing seat 45 and the swing stone 50. The ankle 70 can be continuously rotated so as to follow the following. In this way, the torque transmitted to the escape wheel 60 is directly transmitted to the balance with hairspring 40, so that the balance with hairspring 40 can be supplemented with the torque. When the operating surface 63a of the escape tooth 63 comes into contact with the contact surface 56 of the contact pawl stone 55, the swing seat 45 is located at a stationary position (see FIG. 8) when the balance with hairspring 40 is in a stationary state. Is also located in the second rotation direction M2.

When the escape tooth 63 contacts the contact pawl stone 55 as described above, the escape tooth 63 rotates in the counterclockwise direction M3 while sliding on the contact surface 56, and the contact pawl stone 55 rotates the balance with hairspring 40. Along with this, it gradually moves in the direction in which it separates from the escape wheel gear 64 (the direction in which it retracts from the rotational trajectory R of the escape wheel gear 64). Further, as shown in FIG. 12, when the contact pawl stone 55 is moving in the direction in which the contact pawl stone 55 is separated from the escape wheel gear 64 by the rotation of the balance with hairspring 40, the eject pawl stone 73 rotates the pallet fork 70 counterclockwise. As a result, the rotation locus R of the escape wheel gear 64 begins to enter.

Then, when the contact pawl stone 55 moves to a position deviated from the rotation locus R of the escape wheel 64, the contact pawl stone 55 separates from the escape tooth 63, as shown in FIG. The action surface 63a of the escape tooth 63 comes into contact with the engagement surface 73a of the protruding nail 73 that has entered the rotation locus R of. As a result, rotation of the escape wheel 64 is stopped (first stop). When the contact pawl stone 55 separates from the escape tooth 63, the swing seat 45 is located in the first rotation direction M1 rather than the rest position.

At the initial stage of contact, one of the pallet fork beams 76A of the pallet fork 70 moves toward the dope pin 90 as the pallet fork 70 rotates counterclockwise, but is not in contact with the dope pin 90. There is. Therefore, the pallet fork 70 slightly rotates while the escape wheel 63 and the protruding nail 73 are in contact with each other. When one of the pallet fork beams 76A comes into contact with the dope pin 90, the pallet fork 70 is positioned with its further rotation restricted. Therefore, the escape tooth 63 and the protruding nail stone 73 are in the engaged state. As a result, the pallet fork 70 is stopped, and the escape wheel & pinion 60 is in a state in which the rotation is stopped (second stop). At this stage, the direct torque transmission operation to the swing rock 50 ends.

Thereafter, as shown in FIG. 14, the swing rock 50 separates from the inside of the pallet fork 81 and separates from the pallet fork 70 as the balance with hairspring 40 rotates in the first rotation direction M1. After that, the balance with hairspring 40 continues to rotate in the first rotation direction M1 due to inertia, and the rotational energy thereof is stored in the balance spring 30 as elastic energy. Then, when all the rotational energy is stored in the balance spring 30, the balance with hair 40 stops rotating in the first rotation direction M1 and after resting for a moment, the balance energy is stored in the balance spring 30 and then the opposite second rotation direction. Start rotation toward M2.

As a result, the swing stone 50 starts to move toward the pallet fork 70 again as the balance with hairspring 40 rotates in the second rotation direction M2.
Then, as shown in FIG. 15, when the swing stone 50 enters the uncle box 81 of the pallet fork 70, the swing stone 50 is positioned on the inner side of the uncle box 81 on the traveling direction side of the swing stone 50 with respect to the swing stone 50. While contacting and engaging with the inner surface of the stag beetle 80 side, the pallet fork 81 is pressed in the second rotation direction M2. As a result, the torque of the balance spring 30 is transmitted to the pallet fork 70 through the swing stone 50.

As a result, as shown in FIG. 16, the pallet fork 70 rotates clockwise about the second axis O2 as viewed from the front side, and the one pallet fork beam 76A is separated from the dope pin 90. Further, as the pallet fork 70 rotates, the protruding claw stone 73 moves in a direction in which it separates from the escape wheel gear 64 (a direction in which it retracts from the rotational trajectory R of the escape wheel 64). Then, as shown in FIG. 17, the engaging surface 73a of the protruding claw 73 is moved to a position slightly deviated from the rotational trajectory R of the escape wheel 64, whereby the engaging surface 73a and the escape tooth 63 are moved. The engagement with can be released. Thereby, the stop of the escape wheel & pinion 60 can be released.

Note that, like the entry nail stone 72, the exit nail stone 73 has a pulling angle, so that the escape wheel & pinion 60 is instantaneously retracted in the counterclockwise direction M4 and then transmitted via the front train wheel 12. The torque restarts the rotation in the clockwise direction M3. Then, when the escape wheel & pinion 60 restarts to rotate in the counterclockwise direction M3, as shown in FIG. 18, the escape wheel & pinion 63 has the escape wheel teeth 63 on the sliding surface 73b of the projecting stone 73. Slides and moves relatively, and rotates counterclockwise M3. The torque transmitted to the escape wheel 60 can be transmitted to the pallet fork 70 via the talc stone 73 due to the impact at the time of sliding between the talc stone 73 and the escape wheel 63. Among them, the inner surface of the stag beetle 80 side, which is located on the side opposite to the traveling direction of the swing stone 50, comes into contact with and engages with the swing stone 50. When the escape tooth 63 comes into contact with the engagement surface 73a of the protruding nail 73, the swing seat 45 is located in the first rotation direction M1 rather than the rest position. When the talc stone 73 separates from the escape tooth 63, the swing seat 45 is located in the second rotation direction M2 rather than the rest position.

Therefore, the torque transmitted to the escape wheel 60 can be indirectly transmitted to the balance with hairspring 40 via the pallet fork 70, and the pallet fork 70 can be continuously rotated so as to follow the swing stone 50. In this way, the torque transmitted to the escape wheel 60 is indirectly transmitted to the balance with hairspring 40, so that the balance with hairspring 40 can be supplemented with the torque.

After that, when the pallet fork 73 is moved by the rotation of the pallet fork 70 to a position deviated from the rotation locus R of the escape wheel 64, as shown in FIG. The action surface 63a of the escape tooth 63 comes into contact with the engagement surface 72a of the nail stone 72. As a result, rotation of the escape wheel 64 is stopped (first stop).

At the initial stage of contact, the arm 77 of the pallet fork 70 moves toward the dote pin 90 with the clockwise rotation of the pallet fork 70, but is not in contact with the dope pin 90. Therefore, the pallet fork 70 slightly rotates while the escape tooth 63 and the pallet stone 72 are in contact with each other. Then, as shown in FIG. 20, when the arm 77 of the pallet fork 70 comes into contact with the dope pin 90, the further rotation of the pallet fork 70 is restricted and positioned. For this reason, the escape tooth 63 and the insertion tine 72 are in a engaged state. As a result, the pallet fork 70 is stopped, and the escape wheel & pinion 60 is in a state in which the rotation is stopped (second stop). At this stage, the indirect torque transmission operation to the swing rock 50 ends.

After that, the swing stone 50 separates from the inside of the pallet fork 81 and separates from the pallet fork 70 as the balance with hairspring 40 rotates in the second rotation direction M2. After that, the balance with hairspring 40 continues to rotate in the second rotation direction M2 due to inertia, and the rotational energy thereof is stored in the balance spring 30 as elastic energy. Then, when all the rotational energy is stored in the balance spring 30, the balance with hair 40 stops rotating in the second rotation direction M2, and after resting for a moment, the balance energy is stored in the balance spring 30 and then the opposite first rotation direction. The rotation starts toward M1.

After that, the escapement speed governor 13 repeats the above-described operation with the reciprocating rotation of the balance with hairspring 40. Accordingly, in the escapement 14, in one cycle of the balance with hairspring 40, the direct impact when the escape wheel 64 comes into contact with the contact pawl stone 55 of the swing seat 45, and the escape wheel 64 comes out of the ankle 70. Torque is applied to the balance with hairspring 40 by the two indirect impacts when it contacts 73. That is, the escapement speed governor 13 directly transmits torque through the swing seat 45 that rotates coaxially with the balance with hairspring 40 and rotates around an axis different from the balance with hairspring 40 while the balance with hairspring 40 reciprocates once. While the indirect torque transmission via the pallet fork 70 is alternately performed (switching), the balance with hairspring 40 can be supplemented with power, and the vibration of the escape wheel 60 with a constant vibration corresponding to the balance with hairspring 40 can be achieved. The rotation can be controlled. That is, it can be operated as a semi-indirect-semi-direct impact type escapement 14 that uses both direct impact and indirect impact, and torque transmission is greater than that of a conventional club tooth lever escapement that is an indirect impact type. The efficiency can be increased.

Here, the balance obtained by subtracting the torque applied to the balance with hairspring 40 from the balance spring 30 from the torque applied to the balance with hairspring 40 from the escapement 14 is defined as the balance with balance balance torque.
FIG. 21 is a graph showing a balance balance torque at the end of each impact of the escapement. In FIG. 21, the horizontal axis is the rest position of the swing seat 45 with reference to a predetermined position in the circumferential direction around the first axis O1, and the first rotation direction M1 with respect to the predetermined position is positive. In FIG. 21, the vertical axis represents the balance with balance balance torque at the end of impact. 21. In FIG. 21, the solid line shows the balance with hairspring torque at the end of direct impact, and the broken line shows the balance with balance balance torque at the end of indirect impact. In addition, the balance with torque balance shown in FIG. 21 is for the case where the torque of the barrel wheel 20 is constant.

As shown in FIG. 21, the balance with hairspring torque at the end of the direct impact is larger as the rest position of the swinging stone 50 is located in the first rotation direction M1. That is, as the stationary position of the swinging stone 50 is located in the second rotation direction M2, the balance torque balance tends to be 0 or less when the torque of the barrel wheel 20 becomes smaller. Therefore, the direct impact does not reach the end of the impact, and the operation of the escapement governor 13 is likely to stop. On the other hand, the balance with balance with hairspring at the end of the indirect impact is smaller as the rest position of the rocking stone 50 is located in the first rotation direction M1. That is, as the stationary position of the rocking stone 50 is located in the first rotation direction M1, the balance torque balance is likely to be 0 or less when the torque of the barrel wheel 20 is reduced. Therefore, the indirect impact does not reach the end of the impact, and the operation of the escapement governor 13 tends to stop. For example, when viewed from the axial direction of the first axis O1, in the configuration in which the center C of the rocking stone 50 is positioned on the virtual straight line L in a stationary state, the indirect impact cannot reach the end of impact earlier than the direct impact. ..

In the present embodiment, when viewed from the axial direction of the first axis O1, the center C of the swinging stone 50 of the swing seat 45 in the stationary position is displaced from the virtual straight line L described above by the predetermined angle θ around the first axis O1. The stationary position of the swing seat 45 is set so that the swing seat 45 is arranged in the closed position. As a result, the swing seat 45 is formed (disposed) so that the balance with balance with hairspring at the end of each impact of the escapement 14 becomes even.

FIG. 22 is a graph showing the torque that acts on the balance with hairspring in a direct impact in the escapement governor according to the embodiment. FIG. 23 is a graph showing the torque that acts on the balance with hairspring in an indirect impact in the escapement governor according to the embodiment. In each figure, the horizontal axis represents the rotation angle of the balance with hairspring 40 when the state where the torque of the balance spring 30 is not acting on the balance with hairspring 40 is 0 and the direction of rotation of the balance with hairspring 40 is positive. In each figure, the vertical axis represents the torque applied to the balance with hairspring 40. In each figure, the solid line represents the torque applied to the balance with hairspring 40 from the escapement 14 in the first state in which the mainspring housed in the barrel wheel 20 is fully wound up, and the broken line is contained in the barrel wheel 20. The torque applied from the escapement 14 to the balance with hairspring 40 in the state where the mainspring is unwound from the first state is shown, and the one-dot chain line shows the torque applied from the balance spring 30 to the balance with hairspring 40.

As shown in FIGS. 22 and 23, in the first state in which the mainspring of the barrel complete 20 is sufficiently wound up, the balance with hairspring torque at the end of each impact of the escapement 14 is even. As a result, even if the mainspring of the barrel complete 20 is unwound and the torque applied to the balance with hairspring 40 from the escapement 14 is reduced, the torque at the end of the impact is faster than the other in either the direct impact or the indirect impact. It is possible to suppress the shortage.

Here, as a comparative form, when viewed from the axial direction of the first axis O1, the swinging seat 45 is stationary so that the center C of the swinging stone 50 of the swinging seat 45 in the stationary position is arranged on the virtual straight line L described above. The case where the position is set will be described. FIG. 24 is a graph of a comparative form corresponding to FIG. FIG. 25 is a graph of a comparative form corresponding to FIG.
As shown in FIG. 24 and FIG. 25, in the first state where the mainspring of the barrel complete 20 is sufficiently wound up, the balance with torque balance at the end of indirect impact of the escapement 14 has a balance of balance with balance at the end of direct impact. It is smaller than the torque balance. As a result, when the torque applied from the escapement 14 to the balance with hair 40 becomes small, the balance of balance torque at the end of impact becomes 0 earlier than the direct impact in the indirect impact, and the indirect impact impacts faster than the direct impact. It will not be able to finish.

Therefore, according to the present embodiment, it is possible to prevent one of the direct impact and the indirect impact from reaching the end of the impact earlier than the other. Therefore, the duration of the escapement governor 13 can be improved.

The swing seat 45 rotates integrally with the balance with hairspring 40. Therefore, the torque from the escapement 14 to the balance with hairspring 40 can be efficiently transmitted, as compared with the configuration in which the gears are meshed with each other on the transmission path of the torque from the swing seat to the balance with hairspring.

The escape wheel & pinion 60 contacts the swing seat 45 to transmit torque to the balance with hairspring 40 when the balance with hairspring 40 rotates in the first rotation direction M1, and the pallet fork when the balance with hairspring 40 rotates in the second rotation direction M2. The torque is transmitted to the balance with hairspring 40 by contacting 70. According to this configuration, the escapement 14 can be configured as a so-called semi-indirect-semi-direct impact type, so compared with the case where the escapement is configured as a so-called indirect impact type such as a club tooth lever escapement. Thus, the escapement 14 having excellent torque transmission efficiency can be obtained.

Here, when viewed from the axial direction of the first axis O1, the center C of the swing stone 50 of the swing seat 45 is the first axis O1 and the second axis O1 in the stationary state in which the torque of the balance spring 30 does not act on the balance with hairspring 40. In the configuration in which the balance 40 is arranged on the virtual straight line L passing through the axis O2, the balance with the balance of torque of the balance with hairspring at the end of the impact is different due to the difference in the rotating direction of the balance with hairspring 40 (difference in impact). In the present embodiment, when viewed from the axial direction of the first axis O1, the center C of the rocking stone 50 is arranged at a position displaced with respect to the virtual straight line L around the first axis O1 in a stationary state. According to this configuration, it becomes possible to arrange the swing seat 45 so that the balance with balance with hairspring torque becomes uniform at the end of each impact of the escapement 14. Therefore, the above-described effects can be obtained.

Further, when viewed from the axial direction of the first axis O1, the center C of the rock 50 is stationary, on the third axis O3 side with respect to the imaginary straight line L, around the first axis O1 and more than 0° and 15° or less. It is located at a shifted position. According to this configuration, the escapement governor 13 can be formed such that the swing seat 45 passes through the stationary position during the impact after the stop of the escape wheel & pinion 60 is released. As a result, when the mainspring of the barrel complete 20 is unwound and the torque transmitted to the escape wheel 60 is reduced, the escape wheel 60 stops at the position during impact, so the escape wheel 60 is wound up to the escape wheel 60. It is possible to ensure restartability when the transmitted torque is increased.

The escapement governor 13 includes adjusting means 101, 102, 103 for adjusting the position of the swing seat 45 around the first axis O1. According to this configuration, the swing seat 45 can be arranged so that the balance with balance with hairspring at the end of each impact of the escapement 14 becomes even, so that the above-described effects can be obtained.

In the above-described embodiment, the balance with balance of balance torque at the end of each impact of the escapement 14 is equalized in the first state in which the mainspring is sufficiently wound up. However, the balance with spring balance at the end of each impact of the escapement 14 is wound up more than when the escapement 14 is zero (the escapement 14 is stopped) in at least one of the direct impact and the indirect impact. It should be even in either state.

FIG. 26 is a graph of a modification of the embodiment corresponding to FIG. FIG. 27 is a graph of a modification of the embodiment corresponding to FIG.
As shown in FIGS. 26 and 27, in the present modification, the balance with torque when the impact of each impact of the escapement 14 is completed in a state where the mainspring of the barrel wheel 20 is unwound from the fully wound first state. The balance of payments is even. As a result, when the mainspring of the barrel complete 20 is further unwound, the balance with balance balance torque becomes zero in both direct impact and indirect impact. Therefore, in either one of the direct impact and the indirect impact, it is possible to more reliably suppress the shortage of the torque at the end of the impact earlier than the other.

The present invention is not limited to the above-described embodiments described with reference to the drawings, and various modifications can be considered within the technical scope thereof.
For example, in the above embodiment, the case where the escapement 14 is configured as a so-called semi-indirect-semi-direct impact type has been described, but the configuration of the escapement governor is not limited to this. That is, the escapement is caused by indirect impact when the escape wheel gear comes into contact with the pallet stones of the pallet fork when the balance with hairspring rotates in the first rotation direction and in the second rotation direction. It may be a so-called club tooth lever escapement that applies torque. Even in this case, by arranging the swing rock of the swing seat in the same manner as in the above-described embodiment, the above-described operational effect can be achieved.

Further, in the above embodiment, the escape wheel & pinion 60 has a single-layer structure, but the escape wheel & pinion may have a two-layer structure.

Further, in the above-described embodiment, the escapement 14 includes one pallet fork 70, but the escapement may include an pallet fork unit including a plurality of pallets. The escapement may be configured to apply torque to the balance with hairspring by impacting three or more times in one cycle of the balance with hairspring.

Further, in the above embodiment, the escapement speed governor 13 includes a plurality of adjusting means for adjusting the position of the swing seat 45 around the first axis O1, but at least one of the adjusting means 101, 102, 103 is provided. It should be provided. Further, the adjusting means for adjusting the position of the swing seat 45 around the first axis O1 may include a balance spring 30 and a beard capable of adjusting the fixing position of the balance spring 30. That is, by adjusting the fixing positions of the beard holder fixedly arranged with respect to the balance bridge 16 and the main plate 11 and the outer peripheral portion of the balance spring 30, the balance spring 30, balance 40 and swinging with respect to the balance bridge 16 are adjusted. The position of the seat 45 can be adjusted.

In addition, it is possible to appropriately replace the constituent elements in the above-described embodiments with known constituent elements without departing from the spirit of the present invention.

DESCRIPTION OF SYMBOLS 1... Clock 10... Movement (timepiece movement) 13... Escapement governor 14... Escapement 16... Temp balance (support member) 16a... Outer peripheral surface (circumferential surface) 30... Hairspring 31... Beard ball 34... Holder 35... Beard holder 40... Balance 41... Balance (shaft) 45... Swing seat (torque transmitting member) 46... Swing body (mounting part) 50... Swing stone 60... Squirrel wheel 70... Ankle 101, 102, 103... Adjusting means C... Center of rocking stone L... Virtual straight line M1... First rotation direction M2... Second rotation direction O1... First axis O2... Second axis

Claims (12)

With a hairspring
A balance with the extension and contraction of the hairspring, which reciprocally rotates in a first rotation direction and a second rotation direction opposite to each other about the first axis.
An escapement having an pallet fork that rotates around a second axis and an escape wheel that can be engaged with and disengaged from the pallet,
A torque transmission member that transmits torque from the escapement to the balance with hairspring;
Equipped with
The escapement applies a torque to the balance with at least two impacts in one cycle of the balance with hair,
When the difference between the torque applied to the balance with hair from the escapement minus the torque of the hairspring is defined as the balance with hairspring torque,
The torque transmission member is formed such that the balance of balance with the balance with hairspring is uniform at the end of each impact of the escapement at any time before the mainspring is unwound and the escapement is stopped. Has been
Escapement governor. The torque transmission member rotates integrally with the balance with hairspring,
The escapement governor according to claim 1. The escape wheel & pintle contacts the torque transmission member when the balance with hairspring rotates in the first rotation direction to apply torque to the balance with hairspring, and when the balance with hairspring rotates in the second rotation direction. Torque is applied to the balance with hair by contacting the pallet fork,
The escapement governor according to claim 1 or 2. The escape wheel & pintle contacts the pallet fork when the balance with hairspring rotates in the first rotation direction and rotates in the second direction of rotation, and applies torque to the balance with hairspring.
The escapement governor according to claim 1 or 2. The torque transmission member includes a swinging rock detachable from the pallet fork,
When viewed from the axial direction of the first axis, the center of the swing rock is a virtual straight line passing through the first axis and the second axis in a stationary state where the torque of the hairspring is not applied to the balance with hairspring. On the other hand, it is arranged at a position deviated around the first axis,
The escapement governor according to any one of claims 1 to 4. When viewed from the axial direction, the center of the bobble is arranged at a position displaced by more than 0° and 15° or less around the first axis with respect to the virtual straight line in the stationary state,
The escapement governor according to claim 5. An adjusting unit for adjusting the position of the torque transmitting member around the first axis,
The escapement speed governor according to claim 5 or claim 6. The torque transmission member is fixedly arranged with respect to the balance with hairspring,
The adjusting means is
A support member that rotatably supports the balance with hairspring,
A beard holder fixed to the outer periphery of the hairspring,
Of the support member, a beard support mounted on a peripheral surface extending around the first axis and supporting the beard,
Have
The escapement governor according to claim 7. The torque transmission member is fixedly arranged with respect to the balance with hairspring,
The adjusting means is
With the balance shaft part,
A beard ball attached to the shaft portion and fixed to the inner end portion of the hairspring,
Have
The escapement governor according to claim 7 or claim 8. The balance with hairspring has a shaft portion,
The torque transmission member has a mounting portion mounted on the shaft portion of the balance with hairspring,
The adjusting means is
With the shaft portion of the balance with hairspring,
The mounting portion,
Have
The escapement governor according to any one of claims 7 to 9. A timepiece movement comprising the escapement governor according to any one of claims 1 to 10. A timepiece provided with the timepiece movement according to claim 11.

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